US4715789A - High speed hydraulic fluid venting valve in a hydraulic fluid pump - Google Patents
High speed hydraulic fluid venting valve in a hydraulic fluid pump Download PDFInfo
- Publication number
- US4715789A US4715789A US06/839,977 US83997786A US4715789A US 4715789 A US4715789 A US 4715789A US 83997786 A US83997786 A US 83997786A US 4715789 A US4715789 A US 4715789A
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- US
- United States
- Prior art keywords
- valve
- hydraulic fluid
- bore
- pressure
- valve seat
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
- F16K31/36—Actuating devices; Operating means; Releasing devices actuated by fluid in which fluid from the circuit is constantly supplied to the fluid motor
- F16K31/363—Actuating devices; Operating means; Releasing devices actuated by fluid in which fluid from the circuit is constantly supplied to the fluid motor the fluid acting on a piston
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
- F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
- F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
- F16K17/048—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded combined with other safety valves, or with pressure control devices
Definitions
- the present invention relates to hydraulic fluid pumps and more particularly to hydraulic fluid pumps including a low pressure, high fluid volume pump and a high pressure, low fluid volume pump and having a valve for selectively venting hydraulic fluid to a hydraulic fluid reservoir.
- hydraulic cylinders The use of relatively small hydraulic cylinders is common in many industrial and construction applications. Such applications include Pipe bending, hose crimping, portable hydraulic presses, portable lift jacks, maintenance equipment, etc. Hydraulic fluid is supplied to hydraulic cylinders of such apparatus by relatively portable hydraulic fluid pumps driven by electric motors, small gasoline engines or compressed air motors.
- hydraulic fluid In operation of such hydraulic fluid pumps, hydraulic fluid is forced into a hydraulic cylinder to perform the required work, and then a fluid venting valve will permit return of the hydraulic fluid back to the hydraulic fluid reservoir of the hydraulic fluid pump.
- venting of hydraulic fluid from the hydraulic cylinder is relatively slow and limits the speed of operation of the hydraulic fluid pump.
- the cycle time for the hydraulic fluid pump supplying hydraulic fluid to a hydraulic cylinder of the hose crimping machine may limit the operator's efficiency in swaging couplings on the ends of the hydraulic hoses.
- Prior art hydraulic fluid pumps for use in such applications commonly include an electric motor which drives a low pressure high volume impeller pump and a high pressure low volume piston pump.
- a ball check valve is provided to selectively permit hydraulic fluid to return to the pump reservoir from a hydraulic cylinder supplied with hydraulic fluid by the pump.
- the check valve includes a small diameter passage selectively closed by a ball positioned against a valve seat. The ball is held against the valve seat by a relatively large diameter valve piston housed in a valve cylinder provided in the valve. Hydraulic fluid from the impeller pump is supplied to the valve cylinder to cause the valve piston to apply a seating force on the ball.
- the low pressure impeller pump will maintain a pressure in the cylinder of approximately 120 psi.
- the high pressure piston pump may generate a pressure of 10,000 psi which acts to force the ball away from its valve seat. Accordingly, the surface area of the valve piston must be much greater than the cross sectional area of the valve seat if the 120 psi pressure in the valve cylinder is to be effective to hold the ball against the valve seat.
- the discharge or vent passage and the valve seat of the valve normally have a diameter as small as 0.10 inches. Due to the small diameter of the vent passage, when the hydraulic cylinder is vented, fluid flow through the vent passage is restricted.
- the present invention provides an improved hydraulic fluid pump and an improved hydraulic venting valve embodied in the hydraulic fluid pump.
- the hydraulic fluid venting valve provides for rapid discharge of hydraulic fluid from a hydraulic cylinder and thereby facilitates high speed efficient operation of the hydraulic fluid pump.
- the hydraulic fluid pump embodying the invention includes a valve assembly for controlling discharge of hydraulic fluid from a high pressure hydraulic fluid container to a hydraulic fluid reservoir, the hydraulic fluid assembly having a valve body including a valve bore, and a valve seat.
- a first inlet port communicates with the valve bore on one side of the valve seat, and a first hydraulic fluid outlet port communicates with the valve bore on an opposite side of the valve seat.
- a valve member is housed in the valve bore and is selectively engageable with the valve seat to prevent hydraulic fluid flow through the valve bore.
- Means are also provided for selectively biasing the valve member against the valve seat, the means for biasing including a valve cylinder having opposite ends and a valve piston housed in the valve cylinder.
- valve piston is operably connected to the valve member such that hydraulic fluid pressure in one of the opposite ends of the valve cylinder biases the valve member toward the valve seat.
- Means are also provided for resiliently biasing the valve member away from the valve seat such that the valve member will move away from the valve seat when the hydraulic fluid pressure in the valve cylinder falls below a predetermined pressure.
- valve member is a spool valve having opposite ends, one of the opposite ends of the spool valve defining the valve member engageable with the valve seat.
- the means for resiliently biasing comprises a compression spring engaging an end of the spool valve to bias the valve member away from the valve seat.
- valve member includes sidewalls defining an angle of approximately 15° with respect to the longitudinal axis of the valve bore.
- FIG. 1 is an elevation view partially in cross-section of a hydraulic pump embodying the present invention.
- FIG. 2 is a schematic view of the hydraulic fluid pumping circuit of the hydraulic pump illustrated in FIG. 1 and showing the hydraulic circuit in a fluid pumping mode.
- FIG. 3 is a view similar to FIG. 2 and showing the hydraulic fluid circuit in a fluid venting mode.
- FIG. 4 is an enlarged cross section view of the hydraulic fluid venting valve of the hydraulic fluid pump shown in FIGS. 1-3.
- FIG. 5 is a view similar to FIG. 4 and showing a prior art hydraulic fluid venting valve.
- FIG. 6 is an enlarged illustration of the apparatus illustrated in FIG. 4.
- FIG. 1 Illustrated in FIG. 1 is a hydraulic fluid pump 10 embodying the present invention and including a housing 12 having a reservoir 14 adapted to contain a supply of hydraulic fluid.
- the hydraulic fluid pump 10 includes a low pressure, high volume pump and a high pressure, low volume pump, the low pressure pump comprising a conventional impeller pump 16, and the high pressure pump being comprised of a conventional reciprocating piston pump 18.
- the impeller pump 16 includes a central rotary impeller 20 driven by the shaft 22 of an electrical motor 24, the electric motor 24 being supported by the housing 12. As the electric motor 24 causes rotation of the impeller 20, hydraulic fluid is pulled through a port 26 from the reservoir 14 and is forced through a discharge passage 28 toward a pump outlet connector 30.
- the connector 30 is adapted to facilitate connection of the hydraulic pump 10 to a hydraulic cylinder (not shown) in a conventional manner.
- the high pressure reciprocating piston pump 18 includes a cam 32 supported on the output shaft 22 of the electric motor 24.
- a compression spring 34 surrounds a piston 36 and engages a head portion 38 of the piston 36 to maintain the piston in engagement with the cam 32. Rotation of the output shaft 22 of the electric motor 24 causes rotation of the cam 32 to thereby cause reciprocal movement of the piston 36 of the high pressure pump 18.
- FIGS. 2 and 3 of the drawings The operation of the hydraulic pump of the invention is illustrated schematically in FIGS. 2 and 3 of the drawings.
- the low pressure impeller pump 16 will cause fluid flow through a conduit 28 past a check valve 40 and through a second conduit 42 to the pump outlet port 30.
- the piston pump 18 will also cooperate to draw hydraulic fluid past a check valve 44 from the conduit 28 and to pump hydraulic fluid through a conduit 46, past a check valve 48 and through the conduit 42 to the pump outlet port 30.
- a high pressure fluid relief valve 41 is also provided to vent hydraulic fluid to the reservoir 14 in the event the high pressure piston pump generates a pressure exceeding, for example, 10,000 psi.
- a spring biased check valve 50 will operate to maintain pressure in the conduit 28 of, for example, 350 psi. Once the pressure generated by the impeller pump 16 and by the high pressure pump 18 reaches a predetermined pressure, fluid pressure in conduit 47 will cause plunger 52 to force the ball 54 of check valve 50 away from its valve seat to thereby permit pressure in the conduit 28 to decrease to the pressure established by a second relief valve 56.
- the second relief valve may maintain, for example, 120 psi in the conduit 28.
- the load by the low pressure impeller pump 16 on the motor 24 is then removed to permit the power output of the motor 24 to be used to drive the high pressure piston pump 18.
- the load on the electric motor 24 will increase.
- the load on the impeller pump 16 is reduced and the power output available for operation of the high pressure pump 18 is then increased.
- Means are also provided for venting hydraulic fluid pressure from the hydraulic fluid cylinder when the pump motor 24 is stopped.
- One embodiment of the means for venting is illustrated in FIG. 6 as including a valve assembly 60 including a valve body 62 having a central valve bore 64.
- the valve bore 64 includes a valve seat 66 and houses a valve spool 68 including one end defining a valve member 70 engagable with the valve seat 66.
- Means are also provided for selectively applying a force on the end of a valve spool 68 to bias the valve member 70 into engagement with the valve seat 66.
- the means for applying a force on the end of the valve spool 68 includes a large diameter valve cylinder 72 housing a valve piston 74.
- a fluid port 76 connects the valve cylinder 72 to a passage 78 communicating with passage 28 such that the pressure in the valve cylinder 72 is generated by the impeller pump 16.
- the valve piston 74 acts on the valve member 70 such that hydraulic pressure in valve cylinder 72 and acting on the valve piston 74 applies a force on the valve member 70 to bias the valve member 70 into engagement with the valve seat 66.
- the conduit 42 also communicates with the valve bore 64 intermediate the opposite ends of the valve spool 68 and such that when the valve member 70 is in engagement with the valve seat 66, as shown in phantom in FIG. 6, hydraulic fluid pressure on the opposite ends of the valve spool 68 is balanced.
- this means includes a compression spring 82 housed in the valve bore 64 and engaging an end 84 of the valve spool so as to bias the valve member 70 away from the valve seat 66.
- the force generated on the valve spool 68 by the spring 82 is less than the force on the valve spool exerted by the valve piston 74 when the low pressure hydraulic fluid pump 16 is operating and generating a fluid pressure in the valve cylinder 72.
- hydraulic fluid will drain from the valve cylinder 72 through the impeller pump 16 back to the hydraulic fluid reservoir 14.
- the hydraulic fluid pressure in the valve cylinder 72 will thus decrease rapidly, and the spring 82 will force the valve member 70 away from the valve seat 66.
- the hydraulic fluid in the working hydraulic cylinder can then drain back through the discharge port 30 and through the vent passage 90 to return the hydraulic fluid to the reservoir 14 of the pump.
- valve member 70 is tapered such that the valve seat engaging surface of the valve member is conical and defines an angle of approximately 15° with respect to the longitudinal axis of the valve bore. If the angle of the sides of the conical valve member 70 is substantially greater than 15°, for example, 30° or 45°, the valve member may wear rapidly, and the hydraulic pump will not have an extended useful life. If the angle is substantially less than 15°, the valve member 70 may become wedged in the valve bore 64 and become inoperable.
- FIG. 5 illustrates a prior art venting valve for use in prior art hydraulic fluid pumps.
- the return of hydraulic fluid from the working hydraulic cylinder to the reservoir was provided through a narrow passage 102.
- the hydraulic fluid pressure generated by the impeller pump was conveyed to a valve cylinder 104 housing a valve piston 106.
- the valve piston 106 engaged a ball 108 forcing the ball 108 into engagement with a valve seat 110.
- the present invention is an improvement over the structures shown in FIG. 5, because in the construction shown in FIGS. 2-4 and 6, the bore 64 can be substantially larger than the bore 102 of the FIG. 5 structure, and is sufficiently large that bore 64 can permit relatively unrestricted fluid flow to the vent port 90 and will not delay draining of hydraulic fluid from the working hydraulic cylinder.
- This advantage is achieved because the hydraulic fluid pressure in the valve bore 64 applies a force on both of the opposite ends 70 and 84 of the spool valve 68.
- the hydraulic fluid pressure on the valve piston 74 is not opposed by a force caused by high hydraulic fluid pressure on the valve member 70, and the size of valve bore 64 does not have to be restricted.
Abstract
Description
Claims (6)
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US06/839,977 US4715789A (en) | 1986-03-17 | 1986-03-17 | High speed hydraulic fluid venting valve in a hydraulic fluid pump |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US06/839,977 US4715789A (en) | 1986-03-17 | 1986-03-17 | High speed hydraulic fluid venting valve in a hydraulic fluid pump |
Publications (1)
Publication Number | Publication Date |
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US4715789A true US4715789A (en) | 1987-12-29 |
Family
ID=25281139
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US06/839,977 Expired - Fee Related US4715789A (en) | 1986-03-17 | 1986-03-17 | High speed hydraulic fluid venting valve in a hydraulic fluid pump |
Country Status (1)
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US (1) | US4715789A (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6327920B1 (en) * | 1996-02-09 | 2001-12-11 | C.H. & I Technologies, Inc. | On-line fluid sampling device |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3704588A (en) * | 1971-04-01 | 1972-12-05 | Eaton Corp | Acceleration control valve |
US3889709A (en) * | 1972-10-10 | 1975-06-17 | Massey Ferguson Inc | Hydraulic unloading valve |
US3948147A (en) * | 1972-02-12 | 1976-04-06 | Robert Bosch G.M.B.H. | Hydraulic system with air-venting arrangement |
US3976090A (en) * | 1975-02-25 | 1976-08-24 | Johnson Philip C | Slow start hydraulic valve |
-
1986
- 1986-03-17 US US06/839,977 patent/US4715789A/en not_active Expired - Fee Related
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3704588A (en) * | 1971-04-01 | 1972-12-05 | Eaton Corp | Acceleration control valve |
US3948147A (en) * | 1972-02-12 | 1976-04-06 | Robert Bosch G.M.B.H. | Hydraulic system with air-venting arrangement |
US3889709A (en) * | 1972-10-10 | 1975-06-17 | Massey Ferguson Inc | Hydraulic unloading valve |
US3976090A (en) * | 1975-02-25 | 1976-08-24 | Johnson Philip C | Slow start hydraulic valve |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6327920B1 (en) * | 1996-02-09 | 2001-12-11 | C.H. & I Technologies, Inc. | On-line fluid sampling device |
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Legal Events
Date | Code | Title | Description |
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AS | Assignment |
Owner name: HEIN-WERNER, INC., 1005 PERKINS AVENUE, WAUKESHA, Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNORS:LIEGEL, REINALD D.;BALLARD, JAMES G.;REEL/FRAME:004553/0852 Effective date: 19860401 |
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FPAY | Fee payment |
Year of fee payment: 4 |
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AS | Assignment |
Owner name: FIRST WISCONSIN NATIONAL BANK OF MILWAUKEE, WISCON Free format text: SECURITY INTEREST;ASSIGNOR:HEIN-WERNER CORPORATION;REEL/FRAME:006035/0930 Effective date: 19911220 |
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AS | Assignment |
Owner name: HEIN-WERNER CORPORATION Free format text: RELEASED BY SECURED PARTY;ASSIGNOR:FIRST WISCONSIN NATIONAL BANK OF MILWAUKEE;REEL/FRAME:006184/0334 Effective date: 19920618 |
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AS | Assignment |
Owner name: MCNEIL (OHIO) CORPORATION, MINNESOTA Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:HEIN-WERNER CORPORATION;REEL/FRAME:006723/0368 Effective date: 19920619 |
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REMI | Maintenance fee reminder mailed | ||
LAPS | Lapse for failure to pay maintenance fees | ||
FP | Lapsed due to failure to pay maintenance fee |
Effective date: 19960103 |
|
STCH | Information on status: patent discontinuation |
Free format text: PATENT EXPIRED DUE TO NONPAYMENT OF MAINTENANCE FEES UNDER 37 CFR 1.362 |